JP2002303145A - Internal combustion engine with turbo-charger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an internal combustion engine with a turbo-charger capable of keeping a limit of an engine output high while improving the turbo lag. SOLUTION: A turbine part 31 of a turbo-charger 30 is mounted at a downstream side of a converging part 17 of a cylinder head 11 at an exhaust port 14 in such manner that an axis of rotation m of a rotor shaft 35 of the turbo- charger 30 is orthogonal to the arrangement direction D of cylinders #, and is further positioned on an approximately center in the arrangement direction D of a cylinder head 11. A connecting part 32 is directly fixed at a side of the cylinder head 11 by a bolt to expose the connecting part 32 and a compressor part 33 from the cylinder head 11. A cooling water passage 21 is provided near the exhaust port 14 of the cylinder head 11.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an internal combustion engine with a turbocharger in which at least a part of a turbocharger for supercharging by utilizing the energy of exhaust gas of the internal combustion engine is built in the engine.

[0002]

2. Description of the Related Art Generally, in a turbocharger, a turbine wheel housed in a turbine housing and a compressor wheel housed in a compressor housing are connected by a shaft and provided so as to rotate integrally. Then, the rotation of the turbine wheel due to the exhaust of the internal combustion engine is transmitted to the compressor wheel through the shaft, and this is rotated. By rotating the compressor wheel in this manner, the intake air is compressed, and the compressed intake air is forcibly sent into the combustion chamber of the engine. In the turbocharger, the output of the internal combustion engine is improved by performing supercharging using the energy of the exhaust gas.

In such a turbocharger, the end of the turbine housing on the exhaust side is usually connected to the end on the exhaust side of the exhaust manifold. That is, the exhaust gas discharged from the combustion chamber flows into the turbine housing through the exhaust port of the cylinder head and the exhaust manifold. Therefore, the response performance at the time of acceleration of the vehicle or the like is reduced due to the large volume of the exhaust passage from the combustion chamber of the internal combustion engine to the turbine housing, which causes so-called turbo lag.

Therefore, in order to suppress the generation of such a turbo lag, there has been proposed an internal combustion engine with a turbocharger as described in, for example, Japanese Utility Model Laid-Open No. 63-17832. 4 and 5 show a partial cross-sectional structure of such an internal combustion engine with a turbocharger.

As shown in FIGS. 4 and 5, in this internal combustion engine, the cylinder head 101 is formed so as to be able to be divided into an upper part 101b and a lower part 101c on a dividing surface 101a. The intake port 102 and the exhaust port 103 are formed by assembling the upper part 101b and the lower part 101c. A compressor housing 105 is formed near the opening of the intake port 102 on the combustion chamber 114 side at a position where interference with the intake valve 104 is avoided. On the other hand, the combustion chamber 1 in the exhaust port 103
A turbine housing 107 is formed near the opening on the 14 side at a position where interference with the exhaust valve 106 is avoided. A compressor wheel 108 is housed in the compressor housing 105, and a turbine wheel 109 is housed in the turbine housing 107. The compressor wheel 108 and the turbine wheel 109 are connected by a shaft 110. The shaft 110 is supported by a bearing 111 formed on the cylinder head 101. The compressor housing 105 has a diffuser 112 around the compressor wheel 108.
However, a scroll 113 is formed around the turbine wheel 109 in the turbine housing 107.

As described above, by providing the compressor wheel 108 in the middle of the intake port 102 and providing the turbine wheel 109 in the middle of the exhaust port 103, the volume between the combustion chamber 114 and each of the wheels 108, 109 is reduced. Thus, the turbo lag is improved.

[0007]

However, in the conventional internal combustion engine equipped with a turbocharger, the compressor housing 105 is disposed near the combustion chamber 114, so that the intake air supercharged into the combustion chamber 114 is cooled. This is an extremely difficult structure. That is, the temperature of the intake air adiabatically compressed by the compressor wheel 108 is increased, and the intake air is supercharged to the combustion chamber 114 in a state where its density is reduced. For this reason, the output limit of the engine is naturally lowered, and it has been difficult to obtain desired engine performance.

[0008] The present invention has been made in view of such circumstances, and its object is to improve the turbo lag while improving the turbo lag.
An object of the present invention is to provide a turbocharged internal combustion engine capable of maintaining a high engine output limit.

[0009]

The means for achieving the above object and the effects thereof will be described below. The first aspect of the present invention provides a turbine section that operates based on an engine exhaust flow, and is connected to the turbine section via a connecting section, and also intercepts intake air into a combustion chamber in conjunction with the operation of the turbine section. A part of a turbocharger having a compressor part for supplying the internal combustion engine is a turbocharged internal combustion engine with a built-in turbocharger, and at least a part of a turbine part and a connection part of the turbocharger is provided in an exhaust passage of a cylinder head. The point is that a portion other than the portion provided in the exhaust passage of the turbocharger is provided so as to be exposed from the cylinder head.

According to the above configuration, at least a part of the turbine section is provided in the exhaust passage of the cylinder head.
The volume of the exhaust passage from the combustion chamber of the internal combustion engine to the turbine section is reduced, so that the response performance during acceleration of the vehicle or the like, that is, the turbo lag can be improved. Further, since the entire compressor section is exposed from the cylinder head, the temperature rise of the compressor section can be suppressed. As a result, the cooling efficiency of the intake air supercharged to the combustion chamber can be improved, and the limit of the engine output can be kept high.

According to a second aspect of the present invention, in the internal combustion engine with a turbocharger according to the first aspect, the cylinder head is provided near an exhaust passage provided with at least a part of the turbine section and the connecting section. The gist is that a cooling water passage is provided.

Generally, high-temperature exhaust gas immediately after combustion flows through the turbine section of the turbocharger, so that the turbine section has a high temperature. In this regard, according to the above configuration, since the turbine section is cooled by the cooling water flowing in the cooling water passage, the temperature rise of the compressor section due to radiant heat radiated from the turbine section can be suitably suppressed. In addition, when an intercooler that is generally used to cool intake air that is supercharged into the combustion chamber is used, the size of the intercooler can be reduced.

According to a third aspect of the present invention, in the internal combustion engine with a turbocharger according to the first or second aspect, the internal combustion engine has a plurality of cylinders, and the exhaust passage of the cylinder head is provided in the middle thereof. The exhaust gas discharged from any one of the plurality of cylinders has a merging portion where the exhaust gas merges, and at least a part of the turbine portion and the connecting portion is provided downstream of the merging portion. .

According to the above configuration, since the exhaust passage in the cylinder head plays a role of an exhaust manifold generally used in the prior art, the exhaust manifold can be omitted, and the mountability of the internal combustion engine on a vehicle is improved. Can be. Further, in addition to the exhaust manifold, the gasket disposed between the exhaust manifold and the cylinder head, and the bolts used for coupling the exhaust manifold and the cylinder head are not required, the number of parts can be reduced. it can.

According to a fourth aspect of the present invention, in the internal combustion engine with a turbocharger according to the third aspect, a rotation axis of a turbine wheel housed therein is orthogonal to a direction in which the cylinders are arranged. The gist is that it is provided on the side of the cylinder head in a form.

Generally, a scroll portion is formed in a turbine portion of a turbocharger so as to surround a turbine wheel. Here, the shape of the scroll portion is one of the factors that greatly affect the turbine efficiency of the turbine portion and, consequently, the supercharging efficiency of the turbocharger. That is, if the shape of the scroll portion is not hydrodynamically suitable for the exhaust flow, the energy loss of the exhaust increases, and the turbine efficiency and the supercharging efficiency decrease.

In this regard, according to the above configuration, the internal combustion engine
Since the width of the cylinder in the arrangement direction is larger than the width in the direction orthogonal to the same direction, even if at least a part of the turbine portion is provided in the exhaust passage in the cylinder head, the shape of the scroll portion is suitable for the exhaust flow. It becomes easy to form it into a curved shape.

According to a fifth aspect of the present invention, in the internal combustion engine with a turbocharger according to the fourth aspect, a rotating shaft of the turbine wheel is disposed substantially at a center in an arrangement direction of the cylinders. .

According to the above configuration, it is easy to form the cooling water passages on at least a part of the turbine section provided in the exhaust passage of the cylinder head on both sides in the arrangement direction of the cylinders. For this reason, the turbine section, which has become hot due to the flow of the exhaust gas, can be cooled as a whole, and the cooling efficiency of the intake air supercharged into the combustion chamber can be suitably improved.

According to a sixth aspect of the present invention, in the internal combustion engine with a turbocharger according to any one of the first to fifth aspects, the exhaust passage of the turbine portion and the connection portion of the turbocharger is provided. The point is that parts other than those provided inside are directly fixed to the cylinder head.

According to the above configuration, it is possible to reduce the vibration generated in the turbine section, the connecting section, the compressor section and the like due to the vibration of the internal combustion engine. As a result, the turbo noise can be reduced, and the coupling rigidity of the fastening portions of these portions can be increased, so that the weight and simplification of the fastening portions can be achieved. In particular, when the same configuration is adopted in the configuration of the third to fifth aspects, the position of the bearing portion of the rotating shaft of the turbine wheel is closer to the output shaft of the engine because the exhaust manifold can be omitted. This effect is further promoted. In addition, when the same configuration is further adopted in the configuration according to the first and second aspects, since the temperature rise of the bearing portion and the like are suitably suppressed,
In addition to the above vibration being reduced, the coaxial receiving part,
It is also possible to adopt an air bearing, a magnetic bearing, or the like which has a problem in terms of temperature and vibration. Note that the air bearing entrains air between the rotating shaft and the bearing by the rotation of the rotating shaft, and applies pressure to opposing surfaces of the rotating shaft and the bearing to float the rotating shaft. The magnetic bearing floats the rotary shaft by using a repulsive magnetic force generated by a coil disposed around the rotary shaft.

[0022]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of an internal combustion engine with a turbocharger according to the present invention will be described below with reference to FIGS.
This will be described with reference to FIG.

As shown in FIGS. 1 and 2, the internal combustion engine includes a cylinder block 10, a cylinder head 11 provided above the cylinder block 10, a turbocharger 30, and the like.

The turbocharger 30 is connected to a turbine section 31 that operates based on the engine exhaust flow, via a connecting section 32, and to the turbine section 31.
And a compressor section 33 for supercharging intake air into the combustion chamber 12 in conjunction with the operation of the first section. The turbocharger 30 has a turbine section 31 built in the cylinder head 11. A portion of the turbocharger 30 other than the turbine portion 31, that is, the connecting portion 32 and the compressor portion 33 are disposed so as to be exposed from the cylinder head 11. The center housing 32a of the connecting portion 32 is directly fixed at one end thereof to the cylinder head 11 by bolts 60. The center housing 32a and the compressor housing 33a of the compressor portion 33 are connected to the other end of the center housing 32a. Are connected by bolts (not shown).

In the turbine section 31 built in the cylinder head 11, a turbine wheel 34
It is housed in one exhaust port 14. A compressor wheel 36 in a compressor housing 33a is connected to the turbine wheel 34 via a rotor shaft 35 in a center housing 32a. The rotor shaft 35 is supported by a well-known full float bearing 38 in the center housing 32a, and the turbine wheel 34, the rotor shaft 35, and the compressor wheel 36 can rotate integrally.
In the compressor housing 33a, a spiral diffuser 39 is formed so as to surround the compressor wheel 36.

As shown in FIG. 2, in the present embodiment, the turbocharger 30 has a structure in which the rotation axis m of the rotor shaft 35 is orthogonal to the arrangement direction D of the cylinders # of the internal combustion engine, and It is arranged on the side of the cylinder head 11 so as to be located substantially at the center in the arrangement direction D of the cylinders #.

The cylinder head 11 in which the turbine section 31 of the turbocharger 30 having such a configuration is built has the following structure. That is, the cylinder head 11 is formed with the intake port 13 and the exhaust port 14 connected to the combustion chamber 12 of each cylinder #. The intake port 13 has an intake passage 1 at an end opposite to the combustion chamber 12.
5 is connected, while the exhaust port 14 is connected to the combustion chamber 12.
An exhaust passage 16 is connected to the end opposite to the end.

The exhaust port 14 is branched for each cylinder on the upstream side, and the branched exhaust port 14
Are formed so as to merge at the junction 17. Further, a turbine wheel housing 18 for housing the turbine wheel 34 is formed downstream of the junction 17 of the exhaust port 14. A spiral scroll 19 surrounding the turbine wheel 34 is formed around the turbine wheel housing 18 so as to be continuous with the exhaust port 14. Also, the cylinder head 11 has
An opening 20 for housing the turbine wheel 34 in the turbine wheel housing 18 is formed.

The cylinder head 11 is provided with a plurality of cooling water passages 21 through which cooling water flows near the exhaust port 14. The exhaust port 14 is provided with a bypass passage 22 connected to the upstream side and the downstream side of the scroll 19 and the turbine wheel housing 18 so as to bypass the scroll 19 and the turbine wheel housing 18. In the middle of the bypass passage 22, the upstream portion 2 of the bypass passage 22 is provided.
A waste gate valve 50 is provided for communicating / blocking between the downstream portion 22b and the downstream portion 22b (see FIG. 3). The waste gate valve 50 is attached to the cylinder head 11 from outside.

As shown in FIG. 3, the waste gate valve 50 has a valve portion 51 and a case portion 52. The interior of the case 52 is partitioned by a partition member 53 into a first space 54.
And a second space 55. And the valve part 51
Is connected to the partition member 53 at one end. In addition, the first space 54 has a first through hole 56 and a passage 57.
1 (see FIG. 1) and communicates with the intake passage 15 between the scroll 19 and the intake port 13, while the second
The space 55 communicates with the outside through the second through hole 58. In the second space 55, a bypass passage 2 is provided.
A spring member 59 that urges the valve portion 51 so that the upstream portion 22a and the downstream portion 22b are shut off is housed.

In the internal combustion engine having such a configuration, each cylinder #
When the exhaust gas is discharged from the combustion chamber 12 to the exhaust port 14, the exhaust gas flows into the scroll 19 through the junction 17 of the exhaust port 14. And scroll 19
The exhaust gas flowing into the exhaust passage 16 is discharged to the exhaust passage 16 through the turbine wheel housing 18. When the exhaust gas passes through the turbine wheel housing 18, the turbine wheel 3
4 is rotated. When the turbine wheel 34 rotates in this manner, the rotation is also transmitted to the compressor wheel 36 via the rotor shaft 35, and the compressor wheel 36 rotates. On the other hand, when the compressor wheel 36 is rotated in this manner, the intake air flowing into the compressor section 33 is diffused by the diffuser 39 and the intake passage 15.
And the combustion chamber 12 of each cylinder # is supercharged through the intake port 13.

Here, if the pressure in the intake passage 15 increases due to the supercharging amount of the compressor wheel 36 to the combustion chamber 12, the pressure in the first space 54 of the waste gate valve 50 also increases. . Thus, the first space 5
When the pressure in the first space 54 increases, the partition member 53 is displaced in the direction of arrow A in FIG. 3 against the urging force of the spring member 59 due to the suction in the first space 54, and the valve portion 51 moves Displace in the direction. When the valve portion 51 is displaced in this manner, the upstream portion 22a and the downstream portion 22b of the bypass passage 22 are in communication with each other, and a part of the exhaust gas discharged from the combustion chamber 12 passes through the bypass passage 22. Become. As a result, the amount of exhaust gas discharged from the combustion chamber 12 passing through the scroll 19 and the turbine wheel housing 18 decreases, and the rotational force of the turbine wheel 34 decreases. When the rotational force of the turbine wheel 34 decreases, the rotational force of the compressor wheel 36 also decreases, so that the supercharging amount of the compressor wheel 36 to the combustion chamber 12 decreases. Thus, when the supercharging amount to the combustion chamber 12 decreases, the pressure in the intake passage 15 decreases and the pressure in the first space 54 of the wastegate valve 50 also decreases. For this reason, the valve portion 51 is displaced in the direction opposite to the direction of the arrow A by the urging force of the spring member 59,
The upstream portion 22a and the downstream portion 22b of the bypass passage 22 are shut off.

As described in detail above, according to the internal combustion engine with a turbocharger according to this embodiment, the following excellent effects can be obtained. (1) In this embodiment, the turbine section 31 of the turbocharger 30 is provided in the exhaust port 14 of the cylinder head 11, and the connecting section 32 and the compressor section 33 are provided so as to be exposed from the cylinder head 11. Therefore, the volume of the exhaust port 14 from the combustion chamber 12 of the internal combustion engine to the turbine section 31 is reduced, and the response performance at the time of acceleration of the vehicle or the like, that is, the turbo lag can be improved. Further, since the entire compressor section 33 is exposed from the cylinder head 11, the temperature rise of the compressor section 33 can be suppressed. As a result, the efficiency of cooling the intake air supercharged into the combustion chamber 12 can be improved, and the output limit of the engine can be kept high.

(2) In this embodiment, the cooling water passage 21 is provided near the exhaust port 14 of the cylinder head 11. For this reason, the turbine section 31, which becomes hot due to the flow of the high-temperature exhaust gas immediately after combustion, is cooled by the cooling water flowing in the cooling water passage 21. As a result, the radiant heat radiated from the turbine section 31 causes the compressor section 3
3 can be suitably prevented from rising. When an intercooler that is generally used to cool intake air that is supercharged into the combustion chamber 12 is used, the size of the intercooler can be reduced.

(3) In this embodiment, the junction 17 is formed in the exhaust port 14 of the cylinder head 11, and the turbine section 31 of the turbocharger 30 is provided downstream of the junction 17. For this reason, the exhaust port 14 of the cylinder head 11 plays the role of an exhaust manifold generally used in the related art, so that the exhaust manifold can be omitted and the mountability of the internal combustion engine on the vehicle can be improved. Further, in addition to a turbine housing, an exhaust manifold, and a gasket disposed between the exhaust manifold and the cylinder head, bolts and the like used for coupling the exhaust manifold to the cylinder head are not required, so that the number of parts and cost are reduced. Can be reduced.

(4) In this embodiment, the turbocharger 30 is mounted on the cylinder head 11 such that the rotation axis m of the rotor shaft 35 is perpendicular to the arrangement direction D of the cylinders #.
Placed on the side. Here, in general, in the internal combustion engine, the width of the cylinder # in the arrangement direction D is larger than the width in the direction orthogonal to the direction D. For this reason, even if the turbine part 31 of the turbocharger 30 is provided in the cylinder head 11, the shape of the scroll 19 can be easily formed hydrodynamically in a shape suitable for the exhaust flow. As a result, the energy loss of the exhaust gas discharged from the combustion chamber 12 can be reduced,
It is possible to suppress a decrease in the turbine efficiency of the turbine section 31 and, consequently, the supercharging efficiency of the turbocharger 30.

(5) In this embodiment, the rotation axis m of the rotor shaft 35 of the turbocharger 30 is provided substantially at the center in the arrangement direction D of the cylinders #. For this reason, the turbine section 3 of the turbocharger 30 provided in the cylinder head 11
1, cooling water passages 21 on both sides of the cylinder #
Is easy to form. As a result, the turbine section 31, which has been heated by the flow of the exhaust gas discharged from the combustion chamber 12, can be entirely cooled, and the cooling efficiency of the intake air supercharged into the combustion chamber 12 can be suitably improved. it can.

(6) In this embodiment, the connecting portion 32 of the turbocharger 30 is directly fixed to the cylinder head 11. For this reason, the turbine section 3 caused by the vibration of the internal combustion engine
1, vibrations generated in the connecting portion 32, the compressor portion 33 and the like can be reduced. As a result, the turbo noise can be reduced, and the coupling rigidity of the fastening portions of these portions 31 to 33 can be increased, and the weight and simplification of the fastening portions can be achieved. In particular, since the exhaust manifold can be omitted, the structure of the position of the full float bearing 38 of the rotor shaft 35 of the turbocharger 30 becomes closer to the output shaft of the internal combustion engine, and such an effect is further promoted. Become. In addition, since the temperature rise of the full float bearing 38 and the like are also suitably suppressed, the above-described vibration is reduced, and the air bearing which has problems in terms of temperature and vibration is used instead of the full float bearing 38. It is also possible to employ a magnetic bearing or the like. Note that the air bearing entrains air between the rotor shaft 35 and the bearing by the rotation of the rotor shaft 35, and applies pressure to the opposing surfaces of the rotor shaft 35 and the bearing to float the rotor shaft 35. . The magnetic bearing floats the rotor shaft 35 by utilizing a repulsive magnetic force generated by a coil disposed around the rotor shaft 35.

The configuration of the above embodiment can be changed as appropriate, for example, as follows. In the above embodiment, the waste gate valve 50 is attached to the cylinder head 11 from the outside.
The waste gate valve 50 may be built in the cylinder head 11.

In the above embodiment, the upstream portion 22 a of the bypass passage 22 is connected to the scroll 19 in the exhaust port 14.
The upstream portion 22 a of the bypass passage 22 may be connected in the middle of the scroll 19.

In the above embodiment, the turbocharger 3
0 rotor shaft 35 with full float bearing 38
However, instead of the full float bearing 38, the air shaft or the magnetic bearing may be used to support the rotor shaft 35. In such a case, it is not necessary to supply the lubricating oil to the full float bearing 38, so that it is possible to save troubles such as maintenance of the lubricating oil and to omit a passage through which the lubricating oil flows. it can.

In the above embodiment, the turbocharger 3
0 to the cylinder head 11 with the bolt 6
Although the bolt is tightened at 0, the connecting portion 32 may be fixed to the cylinder head 11 by, for example, clamping.

In the above embodiment, the cylinder head 11 may be configured to be able to be divided into a plurality of members. In the above embodiment, the connecting portion 32 of the turbocharger 30 may be fixed to the cylinder head 11 via a sealing material such as a gasket.

In the above embodiment, the turbocharger 3
The rotation axis m of the rotor shaft 35 of the cylinder 0 is arranged substantially at the center of the cylinder head 11 in the direction D in which the cylinders # are arranged. It may be arranged.

In the above embodiment, the turbocharger 3
The turbocharger 30 is provided so that the rotation axis m of the 0 rotor shaft 35 is orthogonal to the arrangement direction D of the cylinders # in the cylinder head 11. However, if there is a margin in the width of the cylinder head 11 in the direction orthogonal to the arrangement direction D of the cylinders #, the turbocharger 30 is moved in such a manner that the rotation axis m of the rotor shaft 35 is parallel to the arrangement direction D of the cylinders #. A configuration may be provided on the side of the head 11 that is orthogonal to the arrangement direction D of the cylinders #.

In the above embodiment, the cylinder head 11
All the plurality of exhaust ports 14 formed at the junction 17 are joined together. However, the plurality of exhaust ports 14 do not necessarily have to be joined at one joining portion 17. For example, a configuration may be adopted in which an arbitrary exhaust port 14 among a plurality of exhaust ports 14 is joined at one junction and the remaining exhaust ports 14 are joined at the other junction.

When the exhaust ports 14 of the cylinder head 11 are joined at a plurality of junctions, the turbine section 31 of the turbocharger 30 is located downstream of each of the junctions in the exhaust ports 14. May be provided.

In the above embodiment, the number of cooling water passages 21 provided near the exhaust port 14 of the cylinder head 11 is arbitrary. Further, the cooling water passage 21 may be omitted.

In the above embodiment, the turbocharger 3
Although the entirety of the turbine section 31 is provided in the exhaust port 14 of the cylinder head 11, at least a part of the turbine section 31 and the connection section 32 of the turbocharger 30 are provided in the exhaust port 14 of the cylinder head 11. It may be configured.

In the above embodiment, an example of a four-cylinder internal combustion engine is shown as shown in FIG. However, a single cylinder internal combustion engine or a multiple cylinder internal combustion engine other than four cylinders,
The present invention can be similarly applied to an internal combustion engine in which a part of a turbocharger is built. However, when the present invention is applied to a single-cylinder internal combustion engine, the effects described in the above (1), (2) and (6) are obtained.

[Brief description of the drawings]

FIG. 1 is an enlarged partial cross-sectional view showing the vicinity of a cylinder head of an internal combustion engine to which an embodiment of the present invention is applied.

FIG. 2 is a partially enlarged sectional view showing the vicinity of a cylinder head in an enlarged manner.

FIG. 3 is a partially enlarged sectional view showing the vicinity of a bypass passage of the cylinder head in an enlarged manner.

FIG. 4 is a partially enlarged cross-sectional view showing the vicinity of a cylinder head of a conventional internal combustion engine in an enlarged manner.

FIG. 5 is an enlarged partial cross-sectional view showing the vicinity of a conventional cylinder head.

[Explanation of symbols]

10: cylinder block, 11: cylinder head, 12
... combustion chamber, 13 ... intake port, 14 ... exhaust port, 15
... intake passage, 16 ... exhaust passage, 17 ... junction, 18 ... turbine wheel housing, 19 ... scroll, 20 ... opening, 21 ... cooling water passage, 22 ... bypass passage, 22a ...
Upstream part, 22b downstream part, 30 turbocharger, 3
DESCRIPTION OF SYMBOLS 1 ... Turbine part, 32 ... Connection part, 32a ... Center housing, 33 ... Compressor part, 33a ... Compressor housing, 34 ... Turbine wheel, 35 ... Rotor shaft, 36 ... Compressor wheel, 38 ... Full float bearing, 39 ... Diffuser, 50 ... waste gate valve, 51 ... valve part, 52 ... case part, 53 ... partition member, 54 ... first space, 55 ... second space, 56 ... first
Through-hole, 57: passage, 58: second through-hole, 59: spring member, 60: bolt.

──────────────────────────────────────────────────続 き Continued on the front page (51) Int.Cl. ⁷ Identification symbol FI Theme coat ゛ (Reference) F02F 1/36 F02B 37/00 301H

Claims (6)

[Claims] 1. A turbine section that operates based on an engine exhaust flow, and a compressor section that is connected to the turbine section via a connection section and that supercharges intake air into a combustion chamber in conjunction with the operation of the turbine section. A part of a turbocharger having a turbocharger built in the internal combustion engine, wherein at least a part of a turbine part and a connection part of the turbocharger are provided in an exhaust passage of a cylinder head; An internal combustion engine with a turbocharger, wherein a portion other than the portion provided in the exhaust passage of the turbocharger is provided so as to be exposed from the cylinder head. 2. The turbocharged internal combustion engine according to claim 1, wherein the cylinder head is provided with a cooling water passage in the vicinity of an exhaust passage provided with at least a part of the turbine section and the connecting section. An internal combustion engine with a turbocharger. 3. The internal combustion engine with a turbocharger according to claim 1, wherein said internal combustion engine has a plurality of cylinders, and an exhaust passage of said cylinder head is provided with an arbitrary one of said plurality of cylinders in the middle thereof. An internal combustion engine with a turbocharger, characterized in that it has a junction where exhaust discharged from the cylinders merge with each other, and at least a part of the turbine section and the connection section are provided downstream of the junction. 4. The internal combustion engine with a turbocharger according to claim 3, wherein the turbine section is provided on a side of the cylinder head such that a rotation axis of a turbine wheel housed therein is orthogonal to an arrangement direction of the cylinders. An internal combustion engine with a turbocharger. 5. The internal combustion engine with a turbocharger according to claim 4, wherein a rotation axis of the turbine wheel is disposed substantially at a center in an arrangement direction of the cylinders. 6. The internal combustion engine with a turbocharger according to any one of claims 1 to 5, wherein the turbine section and the connection section of the turbocharger other than those provided in the exhaust passage. An internal combustion engine with a turbocharger, wherein a part is directly fixed to the cylinder head.